Record punching machines



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April 10,' 1962 H. A. PANISSIDI 4 Sheets-Sheet 1 PUNCH 55 AcTuAToR 31 GATE VALVE 74 l5. 1L f N 9 5 27\ 6\ 7 37 DIFFERENTIAL se e4 20 VALVE 82 (T3 A4 /25 TT ff- 71 (i CONTROL 33 5o 19 U 22 23 VALVE INVENTOR.

HUGO A. PANISSIDI ATTORNEY April l0, 1962 H. A. PANlsslDl RECORD PUNCHING MACHINES Original Filed May 23, 1957 o FIG.5

4 Sheets-Sheet 2 INVENTOR.

HUGO A. PANISSIDI ATTORNEY April 10, 1962 H. A. PANlsslDl 3,029,013

RECORD PUNCHING MACHINES Original Filed May 25, 1957 4 Sheets-Sheet 3 x Y x Y DTFFERENTIAL x Y VALVE ,PATH OF GATE VALVE WITH MAGNET ENERGIZATION OPEN OPEN iw i UN r--1 CONTROL f L\ Y gEELTJYF VALVE 44 T oF GATE VALVE CLOQF Mx., y

NEUTRAL CLOSED PATH OF GATE VALVE WITH MAGNET DE- ENERGIZATTON K ENERGIZATION l 5 Ms 5 Ms A PUNCH 58 Il Il DISPLACEMENT l l l h l -1.5 Ms 1.5 Ms

9.2 MS 9.2 MS

10.7 MS 10.7 MS

1 cYcLE OF CAM MOVEMENT INVENToR.

HUGO A4 PANlsslDl ATTORNEY April 10, 1962 H. A. PANlsslDl RECORD PUNCHING MACHINES Original Filed May 25, 1957 4 Sheets-Sheet 4 INVENTOR HUGO A. PANISSIDI ATTORNEY itedStates arent 3,029,013 Patented Apr. 1o, 1962 nice 3,029,013 RECORD PUNCHING MACHINES Hugo A. Panssidi, Peekskill, N.Y., assignor to International Business Machines Corporation, New York, NY., a corporation of New York Original application May 23, 1957, Ser. No. 661,112, non Patent No. 2,935,046, dated May 3, 1960. Divided and this application Dec. 31, 1958, Ser. No. 784,215

17 Claims. (Cl. 23d-109) This invention relates generally to machines for punching records and more particularly to the type of punching machine in which hydraulic pulses effect the operation of the punches to punch records. f

This application is a division of the copending application of H.A. Panissidi, Serial No. 661,112, filed May 23, 1957, now Patent No. 2,935,046, granted May 3, 1960.

lt is the main object of the present invention to provide improved means to control the selective transmission or conduction of the hydraulic operating pulses to a driver member for record punch.

A still further object of the invention is to also transmit hydraulic restoring impulses to said driver member to positively restore the latter and the punch.

It is also an object of the invention to design a hydraulic operating system for a card punch wherein reciprocating strokes of the card punch are effected by hydraulic pulses and at a speed greater than that now obtainable by mechanical operations.

A still further object of the invention is to provide a selective transmission of successive pulses to operating and restoring pistons for a punch operating member, one of which puless restores said punch operating member and another of which pulses operates said punch operating member, and to provide a gate valve to control the selective transmission of said operating hydraulic pulses.

Another object of the invention is to provide an electromagnet to effect the opening and time of closing of said gate valve in the novel manner previously described, and to effect its energization selectively, in accordance with the requirement to punch a hole.

The above features of the invention and others which will be visibly apparent as the improvement is understood have been found to be particularly useful in card punching machines in the attainment of higher punch operating speeds. The electromagnetic control of said gate valve is particularly useful and desirable since it enables the incorporation of the present hydraulic improvements in electric card punching machines without destroying the desirale feature of selectivity, i.e. the plugboard control which enables card punching in selected card fields. Therefore, he present improvements may be advantageously embodied in a Well known commercial form of card punching machine, especially in the attainment of higher card punch speeds and with a minimum of structural changes. To more clearly understand the preferred construction of the present hydraulic apparatus when incorporated in a card punching machine, said hydraulic apparatus includes a conventional liquid reservoir with the customary appurtenances, such as fluid gear pump, filter, pressure regulator and accumulator which supplies liquid at a constant pressure from the pressure side of said gear pump to a differential valve unit. The differential valve unit generates hydraulic pulses and is the main source of hydraulic pulses for the punching mechanism. The pulses are timed under control of cams operating the valve unit synchronously with the card punchingand feeding mechanisms. The hydraulic mechanism further includes dual pistons, the cylinders of which are connected to the output ports of the differential valve unit. Upon application of hydraulic pressure pulse from the differential valve unit one of the pistons powers the punch and upon applicacontrol valve 20 ofjthe spool valve type. formed by a cylindrical bore in the `framework 21 of theV punching mechanism to provide a cylinder 22 and includes tion of a hydraulic restoring pulse from the same source the other piston serves to return the punch. The conduction of a hydraulic pressure pulse to each punch operating piston is normally blocked by a respective magnetically controlled gate valve. The gate valves are subject to hydraulic pulses which are generated by a supplemental valve unit to initially open the gate valves by moving the pistons from normal closed position to their open position at which time punch selecting electromagnets may be energized. The gate valves associated with energized magnets have their pistons retained momentarily in open position against the force of the restoring hydraulic pulse. The 'pistons of the gate valves whose electromagnets are deenergized are returned to normal closed position to block the transmission of the hydraulic punch operating pulse. Therestoring hydraulic pulse is delayed to subsequently return the piston associated with an energized magnet back to closed position after the magnet is deenergized. The valve restoring and valve opening hydraulic pulses for said gate valve are preferably supplied by said supplemental valve unit which is operated by cams rotating synchronously with the differential valve unit and the card feeding and punching mechanism.

Other objects of the invention will be pointed out in the following description and claims and illustrated in the accompanying drawings, which disclose, by way of eX- ample, the principle of the invention and the best mode, which has been contemplated, of applying that principle.

1n the drawings: v

FIG. l is a combined view showing diagrammatically and schematically the interconnected components forming the complete hydraulic apparatus constructed according to the present invention.

FIGS. 2-5 represent, on a larger scare than FIG. l, successive positions of the hydraulic differential valves during a complete cycle of operation.

FIG. 6 is a timing diagram illustrating the sequence of events of the hydraulic apparatus shown in FIGS. 1-5 and their interrelation with events occurring in the punching mechanism.

FIG. 7 is a perspective View which shows one possible mechanical construction of the present hydraulic apparatus when incorporated in a well known type of punching machine.

Hydraulic Pressure Unit Referring to FIG. l a liquid holding sump or reservoir 19 is the supply of a suitable fluid for a hydraulic pressure generating means which is preferably in the form of a positive displacement gear pump 11. Through a suitable suction pipe 12 the liquid is withdrawn from reservoir 10 by the pump 11 and is delivered under pressure to a liquid pressure duct or conduit system which includes theliquid pressure conduit 13. Between the gear 11 and conduit 13 there is interposed a check valve 14 to prevent back-flow of pressure should the pump stop, a conventional filter 15, and a pressure regulator valve. 16 adapted to maintain a substantially constant liquid pressure in conduit 13. An'

Control Valve A branch conduit 1S (FIG.V l) of the pressure conduit 13 is connected to a pressure port of a cyclically operated This valve is a shaft 23 carrying lands Vor pistons to be presently l'described. The shaft 23 of the control valve is shifted orv trol valve 20, or more specifically the shaft 23 thereof, is urged to follow the eccentric cam 25 by means of a suitable compression spring 27 fitting in the end of cylinder 22 and bearing against the lefthand end of shaft 23. The control valve includes a central land or piston 3G for alternately directing the How of pressure liquid from the pressure port 19 to a pair of pressure conduits 31 and 32, and a. pair of outer spaced lands or pistons 33 and 34 for forming a communication between each of the conduits 31 and 32 when pressure is applied to the other conduit 31, 32 and respective valve exhaust ports 36 and 37. The latter are connected by respective conduits 38 and 39 to a fluid return conduit 40 seated in the interior of the reservoir 10.

Parallel tluid chambers 41, 42 are formed transversely in the punch framework 21, and between chambers 41, 42 a plurality of cylinders 43 is provided, there being as many cylinders 43 as columns of punching are to be supplied. In the present machine since punching is to be effected in eighty columns, a corresponding number of cylinders 43 and gate valves 44 are provided, all or a plurality of which may be actuated by pulses derived from a single control valve 20.

Each of said gate valves 44, which are also of the spool type, includes a shaft 45 carrying a plurality of pistons 46, 47. The design of the gate valve is the unbalanced pressure type, i.e. whenever pressure is applied to the valve regardless whether it is opened or closed, it will seize for the duration of the applied pressure for a reason to be evident soon.

The shaft 45 of each gate valve has a reduced extension rod 48 to which the armature 50 of a punch control magnet 51 is secured. The action of the control valve 20 is to apply hydraulic pressure to all the pistons 46 to initially shift the gate valves to open position and seal all of the armatures 50 against the yokes 52 of their magnets 50, after which each magnet 51 is energized if punching is to be effected at this particular cycle point. This action occurs repeatedly at a rate of 5600 cycles per minute, so that just prior to punching a hole, which is determined by the energization of a magnet 51, the armature 50 is sealed against the yoke 52 of the magnet 51.

Referring now to FIG. l and the timing diagram of FIG. 6, the above action and operation are effected by movement of piston shaft 23 from a neutral position under control of cam 25, first to the right which positions piston 30 to provide a communication between pressure chamber 19 and conduit 31. which it will be seen terminates in the chamber 41. This provides fluid pressure in chamber 41 and upon each of the pistons 46 to shift all armatures 50 against their respective yokes 52 of magnets 51, in which position each gate valve is open and is retained open if the related magnet 51 is then energized. As piston 34 of the control valve 20 moves to the right under control of cam 25 said piston 34 provides a communication between the exhaust chamber 37 to which the conduit 32 and return conduit 39 are connected. This provides a return of fluid in chamber 42 and conduit 32, which fluid then returns by conduits 39 and 4i) to the reservoir 10.

After valve shaft 23 has been moved by spring 27 to the right under control of cam 25, said cam returns valve shaft 23 to the left and at its extreme lefthand position piston 30 is so positioned that it provides a communication between pressure chamber 19 and conduit 32, whereby uid pressure is now applied to the pressure chamber 42 and to the pistons 47 of all gate valves, thus shifting the valve shafts 45 of all those gate valves back to closed position shown in FIG. l whose magnets 51 are not energized at this time. The path of the gate valve to closed position with magnet deenergization is shown in FIG. 6. During this operation the piston 33 of the control valve is now positioned so that it provided a communication between chamber 41, conduit 31 and exhaust chamber 36, enabling free return of the liquid to the reservoir by return conduits 38 and 40.

The magnets 51 which are energized during this operation overcome the hydraulic pressure applied to the pistons 47 of the gate valves and retain the gate valves open. When any gate valve is open the piston 47 is in such position that it permits a hydraulic work pulse to be applied to a hydraulic punch motor, as will soon be described. It is evident then that if an electrical impulse is applied to the magnet at the time when the magnet armature 50 and yoke 52 are mechanically sealed, the return stroke of the gate valve will be delayed suiciently to permit the hydraulic pulse from the differential valve to actuate the punch pistons 61. Referring to FIG. 6 timing chart, it will be noted that the gate valve is delayed or urged to the left during a period of 5 milliseconds after the electromagnet is deenergized.

It will be evident then that the magnets 51 accomplish no work in actually opening and closing the respective gate valves 44, since this is effected by alternating hydraulic pressure pulses derived from control valve 20. The magnets 51 merely determine whether the gate valves are to be immediately restored to their normal closed position, or are to be retained in their open position to enable the hydraulic work pulse to be applied to the punch motors or actuators.

Punch Actualor The punch actuator preferably comprises for each order a rockable plate 55 pivoted on a rod 56 carried by the punch framework. Plate 55 has an open slot receiving a pin 57 of a punch pin 58 adapted when elevated to pass through a hole in a die plate 59 and a stripper plate 60 to punch a hole in the selected index position of the card column.

Loosely fitting in valve cylinders in the punch framework is a pair of pistons 61, 62, the outer ends of which pistons 61, 62 bear against the lower and upper ends of the rockable plate 55. The inner ends of said pistons 61, 62 are subjected to alternate hydraulic pressure pulses from respective pressure chambers 63, 64, as Will be presently described.

It is desirable to limit the stroke of the punch actuator 55 in both directions of travel, therefore, a pair of adjustable stop members 65, 66 carried by the punch framework is provided and abut the inner ends of pistons 61, 62 respectively. As shown in FIG. l, the operating punch piston 61 is normally held againstthe lower stop 63 by the liquid pressure applied from the pressure restoring chamber 64.

Differential Valves Any suitable hydraulic pulse means for rocking the punch actuators 55 may be provided. However, a hydraulic valve mechanism shown in FIGS. 1-5 is preferred. FIG. 6 shows its timing diagram. As shown in FIGS. l5 a pair of synchronized eccentric cams 70 and 71 provided with the proper phase angle difference, individually operate related control valves 72 and 73 in a predetermined manner to convert fluid supplied by the constant pressure conduit 13 to pulses applied alternately to conduits 74 and 75. This cyclic operation is timed synchronously with the gate valve 44, the control valve 20, the energization of magnets 51 and other timed elements. The hydraulic mechanism referred to above and which will be described herein in a general manner is fully described and claimed in the application of Hugo A. Panissidi, Serial No. 479,111, led December 31, 1954; now Patent No. 2,800,885, issued July 30, 1957.

From FIG. 1 it will be seen that extending from the upper valve 72 are the conduits 74 and 75. Conduit 74 terminates at one end as a connection to a transverse chamber 76 inthe punch framework 21. From chamber 76 there is a plurality of aligned bores 79, 80, one for each punch actuator 55, said bores being normally cut off from each other by the piston 47 of the gate valve in its closed position, as shown in FIG. 1, or having a uid communication with each other when piston 47 has been shifted to its open position, as has been described. With this construction when gate valve 44 is open, hydraulic pressure is carried from bore 79 to bore S0 and applied to the pressure chamber 63. The applied hydraulic work pulse will shift piston 6l and rock punch actuator 55 clockwise to elevate punch pin 58 to punch a hole in a well known manner. At this time valves 72, 73 are in such position that a return from conduit 75 is made to return conduit 4t2'. Valves 72 'and 73 then generate a hydraulic pulse over conduit '7S which is connected to pressure chamber 64 and places pressure on said charnber 64 and piston 62, thus restoring punch actuator 55 and punch 58, if the latter has been previously actuated to punch a hole. At this time piston 47 of the gate valve is in such position that a liquid return may be effected from chamber 63, bores Si), 79, conduit 74, and through valves 72, 73 to return conduit 46.

As has been described, in order to cyclically reciprocate the control valves 72 and 73 to convert liquid under constant pressure to pulses to be directed to the punch operating chamber 63 and punch restoring chamber 64, respectively the pair of shaft-driven rotatable eccentric cams 70 and 7l, respectively are provided for said control valves. These eccentric cams engage piston rods of their related control valves 72 and 73, and are effective to alternately reciprocate the control valves in a predetermined manner dependent upon the eccentric formation of said cams. Disposed on the opposite side of the piston rod of each control valve is a suitable compression spring 81 (see FIG. l) to continuously urge the piston rods against the related cams to follow the same. The cams 70 and 71 may be mechanically driven by any suitable means for synchronous rotation.

For a better understanding of the operation, FIGS. 2 to 5 show the various extreme positions of the control valves 72 and 73 during certain portions of their cyclic operation.

As shown in FIG. 2, the second control valve 73, having followed its cam 71, is at the right to position the central control piston 82 and end pistons 83 and 84 for enabling the punch operating pressure chamber 63, bores S0, 79, pressure chamber 76 (FIG. l) to drain by means of the conduit 74, chamber 85, the open central port 86 which leads to the chamber 87 in the first control valve 72, the drain port 8S, and return conduit 40. At this time the pistons 47 of the gate valves (FIG. l) are at the left to enable communication between bores 79 and With the second control vvalve 73 in the position shown in FIG. 2 the eccentric cam 70 has earlier permitted the rst control valve 72 to shift to the position shown in FIG. 2 wherein its central piston 90 is at the left. In this position, the pressure port 93 connected to pressure duct 13 directs liquid under pressure to the right through the chamber 94 and channel leading to the now open rightha'nd port 95 of the second control valve 73, which in turn directs the liquid through the associated chamber 96 and conduit 75 to the restoring drive chamber 64 of the punch restoring pistons 62. Thus, it can be seen that during the conditions above described, the operating piston 6l and thus the punch actuator S5 are maintained in their retracted positions by the liquid under pressure and that the conduit 74 is directly connected to drain through the open exhaust port SS. The above positions ot the valves '72 and 73 represent the dwell time interval indicated from Y-X in the timing chart during the first and second half cycles of cam rotation.

As the eccentric cams rotate in synchronism, with the second cam 7l lagging the first cam 7i) by a phase angle difference of 40, the point is reached wherein the first cam 7i) shifts the iirst control valve 72 to the right, as shown in FIG. 3. As its shifting central control piston 9i? reaches the point X, lFIG-f. 6, the liquid under pressure is transferred or redirected at the pressure port 93,; to the lefthand chamber 87 which communicates with the central control port 86 of the second valve 73. Since valve 73 has not changed in FIG. 3 its position from that shown in FIG. 2 the liquid passes through the chamber 85 and over 'the conduit 74 to the pressure chamber 76, thence by bores 79, 'Staand open gate valve 44 to pressure chamber Y 63. This is effective in the event that a gate valve has been retained opened by energization of its magnet 51 to drive the punch piston 6I rapidly to the left, following the curve E of FIG. 6 to perform the punching operation. Gr" course, as the rst control valve 72 shifts to the right, the righthand exhaust port 98 is opened (see FIG. 3) to enable the displaced liquid in the chambers 64 to drain through conduit 75, port 95, the channel to chamber 94, port 98, branch drain conduit 99, to drain conduit 40, as shown by the arrows in FIG. 3.

Approximately 1.5 milliseconds after the first control valve 72 shifts to the right and passes over its cutoff or neutral position, represented as the time period X-Y on the 'timing chart, the cam 71 shifts the second control valve 73 to the left or in the opposite direction so that the central piston S2 cuts olf the supply of liquid to the 'operating chamber 76 at the point Y, shown in the` timing chart. yFurther travel to the left redirects the liquid under pressure supplied to the port 36 through the chamber 96 and the retraction conduit 75 to the retraction chamber 64. This quickly returns the punch piston 61 against its stop 65 in the retracted position. The shifting action of the second control valve 73, of course, cuts olf the righthand port g5 to prevent discharge to drain and at the same time connects the operating piston chamber 76 and conduit 74 to the left hand port lili) which is now connected to drain through the passage leading to the righthand exhaust port 98 of the first control valve 73, as shown by the arrows. With the pistons as shown in FIG. 4, it is obvious the punch will be held retracted in the same way as effected by the valve position in FIG. 2, but the control pistons of both valves have been transferred to the opposite sides of their pressure ports. This represents the completion of a half cycle of cam and valve movement.

As the cams continue their rotation, the second control valve 73 is maintained with the righthand side of the port 86 open, however, the first control valve 72 now shifts to the left, as shown in FIG. 5. After its cutott position is reached at the point X, continued travel opens the righthand side of the pressure port 93. Thus, liquid under pressure is redirected to the right chamber 94, passes through the channel leading to the now open lefthand port fitti? of the second control valve 73, continues through the chamber and conduit 74 and is applied at the pressure operating chamber 76 to againV- `shift the punch piston 61 to the left. Upon punch piston movement to the left, the liquid in the retraction chamber 64 is displaced, passes through the return conduit 75, chamber 96, the central port 66 of the second valve 73, the channel leading to the chamber 87 in the first valve 72 and the lefthand exhaust port 88 to drain, as clearly central port 86, the connection to the lefthand exhaust' port 3S in the first control valve 72, to the drain conduit 40. As this occurs, of course, the righthand port of the second control valve 73 is opened which immediately l applies liquid under pressure to the retraction chamber 64, as indicated by the arrows in FIG. 2 to return the punch to its normal position. Thus, the valves have now completed a fully cycle as indicated on the timing diagram, FIG. 6. This end of a full cycle position corresponds to the differential valves positions shown in FIG. 2 and further valve operations from this point would be repeated in a cyclical manner.

In this particular embodiment, the eccentric cams 79 and 71 are rotated synchronously with operations of the punch selecting mechanism including the time of energi- Zation of magnet 5l. The hydraulic pressure impulses directed from the differential valves to the punch piston 61 occur twice for each complete revolution of the eccentric cams 70 and 71. This timing is exactly in agreement with two operations of the punch selecting mechanism. This is shown in the timing chart of FIG. 6 wherein each hydraulic pulse transmission is timed to occur irnmediately after each magnet energization. Of course, if the punch selection is set up at a high or lower rate, the speed of operation of the eccentric cams would be varied accordingly.

Any suitable gear reduction ararngement (not shown) may be provided to positively drive the valve cams 70 f and 71 in synchronism with the punch selecting mechanism.

From FIG. 6 it will be observed that during the Y-X period of each half cycle while the punch actuators 55 are being restored the control valve 44 first transmits a hydraulic pressure pulse in the duct or conduit 31 and pressure chamber 4l to drive the gate valves open and to seal the armatures 50 against the yokes of their magnets 51. This operation (timing L) ensues just prior to the transmission of the electrical pulse K to energize magnet 51. The control valve then reverses (timing M) to apply hydraulic pressure in duct 32 after such energization to restore the gate valves for those orders in which the magnets 51 are unenergized. The retention of each gate valve, when a magnet is energized, is shown by the dotted line timing N, Whereas, for the unenergized magnets the gate valves return, ase shown by the full line timing M. It will also be observed that during each hydraulic pulse period X-Y, the gate valves are retained opened, and the magnets 51 are still energized, as shown by the 5 millisecond time of energization of the magnet 51. The time of the reciprocation of the punch (timing E) is synchronized with the hydraulic pulse period X-Y in each half cycle, thus, conforming to the requirement that a magnet 51 effectively retains its related gate valve closed at the time control valves '72, 73 transmit a hydraulic punch operating pulse to effect, in the same hydraulic pulse period, the punch displacement.

Card Punching Machine The present improvements may be embodied with advantage in a card punching machine of the type shown in FIG. 7 which is well known and disclosed in numerous patents, among which the patent to C. D. Lake, No. 2,032,805 may be referred to. FIG. 7 also discloses how the preferred construction of the hydraulic punch operator and electromagnetic control therefor is designed in such manner that it ts in the above type of card punching machine.

The above form of punching machine comprises a read side and a punch side. Only the latter is generally shown in FlG. 7 to understand by way of example how the electromagnetic control of the hydraulic punch operator by read brushes for pattern cards enables their duplication on blank cards by the improved hydraulic punch operator at an increased speed.

The stack of cards 10S, which are obviously in a hopper, comprise for each group a pattern card and a following group of blank cards which are fed by a card picker to feed rolls 166, and then to a reading station comprising X sensing brushes 167 and a contact roller 108, neither of which specifically enters in the present improvement. The cards are then fed by a pair of rollers 109 to the punching mechanism. The punched cards are thereafter engaged and fed by rollers 110 to a pattern read station comprising brushes 111 and a contact roller 112. The punched cards are then fed by feed rollers 113 to a storage hopper, reference character 114 representing a stack of punched cards which would be fed therein.

As is well known, holes in the pattern card are analyzed by brushes 111, closing a circuit diagrammatically shown for one order as from line L, contact roller 112, through bursh 111, Wire 115, magnet 51 to line L. When a brush 111 sensesa hole in an index point of a pattern card the corresponding index point of a following blank card is beneath the punch 58, and a result of the energization of the magnet 51 and the operation of the hydraulic punch operator the blank card is punched at a high speed. After the first blank card has been punched it acts as a pattern card for the following blank card of the group, as is well known in this form of card punching machine.

The card punching shown in the aforesaid patent to Lake No. 2,032,805 employs a mechanical Geneva drive for the card feed rolls to effect a step by step in operation. it is well adapted for lower punch speeds but for the present machine to obtain the full advantage of the higher punch speeds obtainable by the present improvement, it is desirable to employ an intermittent or step by step hydraulic feed roll drive. The latter is generally shown herein and identified by reference numeral 116. Details of this form of intermittent hydraulic drive are shown and claimed in the application of H. A. Panissidi, Serial No. 661,113, filed May 23, 1957, which issued as Patent No. 2,902,005.

Referring to FIG. 7 the stripper plate 59 consists of a transverse channel member and the cooperating punch die 60 consists of a plate supported by transverse plates 120. Below said punching mechanism there is provided a dual set of sandwiched assembled plates, designed with a view of providing the necessary conduits by channeling the face of the plates, and the necessary hydraulic pressure chambers by transverse milled slots, as will soon be evident. For each side there is a series of plates 121-125.

Transverse chamber 64 is formed by milling or channeling plates 122, 123. Pistons 61, 62 are also slidable in said plates 122, 123. Magnets 51 are carried by the outer cover plate 125, the ve assemblies of eight magnets being assembled 0n one side and another similar assembly being assembled on the other side, thus enabling the eighty magnets for rows to be widely spaced, and the punches close together for narrow column punching. FIG. 7 also Vshows clearly the formation of the plates 122, 123, 124 to provide cylinders for the gate valves 46, 47, and related conduits 31, 32, 79, 80 and pressure chamber 76, which latter has the duct connection 74 to the differential valves 72-73. The series of differential and control valves are assembled in a liquid tight chamber 126, and are driven by intergeared parallel shafts 127. The hydraulic power supply, reservoir, etc. are not shown in FIG. 7 since they are a unit assembled apart from the punching unit, and having only conduit connections thereto, as clearly shown in FIG. 1.

While there have been shown and described and pointed out the fundamental novel features of the invention, it will be understood that various omissions and substitutions and changes in the form and details of the device illustrated and in its operation may be made by those skilled in the art, without departing from the spirit of the invention. It is the invention, therefore, to be limited only as indicated by the scope of the following claims.

What is claimed is:

1. In a machine for selectively pcrforating records, a punch adapted when moved in one direction to punch a hole and in another direction to be positively restored, a pivoted rockable member connected to said punch, a casing having a pair of piston chambers, a pair of pistons disposed in said piston chambers and abutting said rockable member above and below its pivot, and means for directing lluid pressure from a source first to one piston chamber to move one piston to rock the member and said punch in said one direction, and then to the other piston chamber to cause the other piston to rock said member and punch in said other direction to positively restore said punch.

2. The combination claimed in claim 2 wherein the movement of either piston by fluid pressure will cause said rockable member to move the other piston in the related piston chamber to displace and return the fluid therein through an opening, and said fluid pressure applying means comprises; control valves, means for applying iluid pressure to said control valves, means for moving said valve, and fluid directing means controlled byy said valves communicating with said piston chambers, tor directing in one position of said valves effected by said moving means duid pressure to the chamber of the piston which rocks the punch to punch a hole and for opening the piston chamber of the other piston which restores the punch to enable the return of the iluid in the related chamber, and in the other position of said valves etlected by said moving means for then directing fluid pressure to the chamber of the piston which restores said punch and for opening the piston chamber of the piston which rocks the punch to enable the return of the fluid in the related chamber.

3. A machine for selectively perforating records comprising a punch moved in one direction to punch a hole, a pivoted rockable member connected to said punch, a casing having a pair of piston chambers, a pair of pistons therein having their faces outside of said chambers abutting said member above and below its pivot whereby the movement of either piston in its chamber will move the other piston to displace fluid therein, valve means for admitting uid pressure successively to the piston chambers to move the pistons successively whereby the piston below said pivot rocks said member and said punch in said one direction, and the piston above said pivot rocks said member and said punch in the other direction, and a tuid conducting conduit means comprising a pair of conduits between said valve means and openings in said pair of piston chambers to cause said valve means to direct fluid pressure through one conduit to the chamber of one piston, and simultaneously open the piston chamber of the other piston to effect the return of displaced lluid therein by the other conduit. p 4. A machine for selectively perforating records co-mprising a punch adapted to move in one direction :to punch a hole, a pivoted rockable member connected to said punch, a casing having a pair of cylindrical bores therein comprising piston chambers, a pair of pistons, each disposed in the related piston chamber and having portions exterior of the piston chambers abutting said member above and below i-ts pivot, valve means for admitting uid pressure from a source alternately to said piston chambers to cause said piston below said pivot to rock the member and said punch in said one direction to punch a hole, and then to the other piston chamber to cause the piston above said pivot to positively rock said niember and punch in another direction to restore said punch, and a fluid directing system interconnecting said valve means and said chambers for transmission of iluid pressure alternately to said piston chambers.

5. In a hydraulically operable punching machine, a punch with which the index points of a record are coordinated in succession, a casing having a pair of piston chambers, a pair of pistons in said chambers, means operated by one piston to operate said punch to punch a hole and operated by the other piston to restore said punch, hydraulic pulse generating means for transmitting at each index point a hydraulic pulse to the piston chamber of said one piston, a gate valve adapted to be opened to cause the transmission of said hydraulic pulse to the piston chamber of said one piston, means to open said gate valve to cause the transmission of the hydraulic pulse to the piston chamber of said one piston to cause said one piston to eitect the operation of said first named means to operate said punch at a selected index point of the record, and means to thereafter transmit a hydraulic pulse to the piston chamber of said other piston to cause said other piston to eiect the operation of said irst named means to restore said punch.

6. In a hydraulically operated punching machine, a series of punches with which the index points of a record are coordinated in succession, hydraulically operated means for operating each punch, hydraulic pulse generating means for generating successive discrete hydraulic pulses one for each index point and for transmitting a hydraulic pulse to said hydraulically operated punch operating means, a gate Valve controlling the transmission of one of the hydraulic pulses to the hydraulically operated punch operating means and having a closed position and an open position, electromagnetic means, and means for energizing saidv electromagnetic means at a time dependent upon the index point to be punched for causing the opening of the related gate valve `to cause the transmission of the one of the successively generated hydraulic pulses to operate the hydraulically operated punch operating means to punch the record.

7. ln a hydraulically operable punching machine for hydraulically effecting punching of a record, a punch, a hydraulic punch operator for said punch, means for 'generating and transmitting a pulse to actuate Asaid hydraulic punch operator to actuate said punch, a gate Valve adapted to have a closed position and also an open position for permitting the transmission of said pulse to said hydraulic punch operator, means for generating and -transmitting successive hydraulic pulses to said gate valve to initially shift said gate valve to an open position from a closed position, an electromagnet adapted to be energized to select the index point to be punched, and means controlled by said electromagnet when energized .to retain the gate Valve in open position against the force of the hydraulic pulse for closing said valve.

8. ln a cyclically operable punching machine, a series of punches with which the plurality of index points of a record are coordinated in succession, a plurality of hydraulic punch operators one for each punch, hydraulic pulse generating means for transmitting at each index point a hydraulic pulse. to each punch operator, a plurality of gate valves controlling said hydraulic punch operators and each having a closed position and an open posmon for transmission of said hydraulic pulse, means for transmitting hydraulic pulses to said gate valves to open all of said gate Valves prior to punching each index point and then to close said gate valves, and electromagnetic means energized at selected cycle points dependent upon the index point to be perforated for retaining the related gate valve open against the force of the hydraulic pulse wh1ch would close said gate valve.

9; In a cyclically operable punching machine for punching arecord, a punch, a hydraulic punch operator and restorer for said punch, means for generating and transmitting successive hydraulic pulses, the rst pulse to actuate said hydraulic punch operator to actuate said punch and then a secondy pulse lto positively restore said punch, a gate Valve controlling said hydraulic punch operator adapted to be moved from a closed posi-tion to an open position for permitting the transmission of said first pulse, means for generating and transmitting successive hydraulic pulses `to said gate valve to initially shift said valve to an open position and then to a closed position, an electromagnet for controlling said gate valve, and means controlled by said electromagnet when energized to retain the gate valve in open position against the force'ot the hydraulic pulse for closing said valve.

10. In a cyclically operable punching machine for' punching selected index points of a record, a punch, hydraulic punch operating and restoring means operable by successive pulses, means for generating and transmitting successive hydraulic pulses for each index point, the first pulse to said hydraulic punch operating means to actuate said punch and then a second pulse to positively restore said punch, a gate valve adapted to have an open position for permitting the transmission of said first pulse and a closed position, means for generating and transmitting successive hydraulic pulses to said gate valve for each index point to initially shift said gate valve to an open position and then to a closed position when said gate valve is not restrained, an electromagnet energized at -times corresponding to the index points when said first pulse is transmitted to select the index point to be punched, and means operable by said electromagnet when energized to restrain the gate valve from moving to a closed position by -the force of the hydraulic pulse for closing said valve, whereby said gate valve is kept open for transmission of said first pulse to the hydraulic punch operating means.

l1. ln a machine for selectively perforating records, a punch adapted, when moved in one direction, to punch a hole and, in another direction, to be positively restored; a pivoted rockable member connected to said punch; a casing having a pair of piston chambers; a pair of pistons disposed in said piston chambers and abutting said rocl able member above and below its pivot; and means for selectively directing fluid under pressure from a source to one piston chamber to move one piston to rock the member and said punch in said one direction, and means for cyclically admitting fluid under pressure to the other piston chamber to cause the other piston to rock said member and punch in said other direction to positively restore said punch.

l2. A high speed punch apparatus comprising a plurality of punching members, fluid pressure actuated means associated with each of said punching members, an enclosed manifold to contain an actuating fluid, means to alternately apply and release pressure to said actuating fluid according to a predetermined timing cycle, channel means communicating each of said fluid pressure actuated means with said manifold, valve means associated with each of said channel means to normally maintain each channel means closed, another fluid means to open automatically predetermined ones of said valve means, and means to hold open said predetermined ones of said valve means so as to allow a subsequent actuating fluid impulse to actuate the associated punching members.

13. A high speed punch apparatus comprising a punching member, fluid means adapted to actuate said punching member according to a predetermined schedule, a first valve means interposed between said punching member and said fluid means for controlling the actuation of said punching member by said fluid means, an extended portion on said first valve means, a piston forming part of said extended portion, a source of control fluid for actuating said first valve member through contact with said piston, a second valve means interposed between said piston and said source of control fluid for controlling actuation of said first valve member by said control fluid, and means to control said second valve member in timed relation with said predetermined schedule.

14. A high speed punch apparatus comprising a plurality of punching members, fluid pressure operated actuating means associated with each of said punching members, an enclosed manifold to contain fluid, channel means communicating each of said fluid pressure actuating means with said manifold, valve means associated with each of said chanel means to normally maintain the channel means closed, fluid means for shifting said valve means, and selectively operable magnetic means for overriding said fluid means to hold said valve means in a predetermined shifted position.

15. A high speed punch apparatus comprising a punching member, fluid pressure operated actuating means associated with said punching member, a fluid supply, channel means to communicate said fluid supply with said fluid pressure operated actuating means, valve means interposed between said fluid supply and said fluid pressure operated actuating means, means for applying and releasing pressure on said fluid supply to develop fluid impulses to aetuate said actuating means when said valve means is open, means for first enabling and then disabling said valve means in respect to its ability to pass fluid impulses to the fluid pressure actuating means, and selectively operable magnetic means for overriding the disabling of said valve means.

16. A high speed punch apparatus comprising a punching member, a fluid pressure operated actuating means associated with said puncnnig member, a fluid supply, means to apply and release pressure on said fluid supply, channel means to communicate said actutaing means with said fluid supply, valve means positioned within said channel means to maintain said channel means normally closed7 selectively operable magnetic means associated with said valve means to control the same so that said channel means remains open when said valve means has been operated to open said channel, and means operable to cause said valve means to open said channel whereby said punching member is actuated by said fluid when pressurized if said magnetic means is operated to hold said valve means to open said channel.

17. A high speed punch apparatus comprising a punching member, fluid means for actuating said punching member, an enclosed manifold for containing said fluid means, channel means to communicate said fluid means with said punching member, fluid operated actuating valve means to maintain said channel means normally closed to prevent communication of said fluid means with said punching member, means to apply and release pressure on said fluid means according to a predetermined schedule. and control valve means for controlling the passage of fluid for the actuation of said actuating valve means whereby said actuating valve is operated to open said channel means to communicate said fluid means with said punching member once said control valve means permits passage of fluid for the actuation of said actuating valve means.

References Cited in the tile of this patent UNITED STATES PATENTS 539,573 Cartwright May 2l, 1895 1,978,966 Sprague Oct. 30, 1934 2,643,677 MacLean June 30, 1953 2,800,885 Panissidi July 30, 1957 

